Multiple automatic pattern controlled milling machine



March 15, 1938. ROEHM 2,111,332

MULTIPLE AUTOMATIC PATTERN CONTROLLED MILLING MACHINE Filed April 23, 1957 ll Sheets-Sheet 1 Q INVENTOR.

/;FA///Y famw ATTORNEY.

E. G. ROEHM March 15, 1938.

MULTIPLE AUTOMATIC PATTERN CONTROLLED MILLING MACHINE Filed April 23, 1957 ll Sheets-Sheet 2 4 N M m Y 0 E m m W m 1% k W m Q Q 1% mwi m 1% no 0 oo o w: M $1 M Q \m. Q3. W 00 oo 00 I 00 1'? \Nm w M \Q\ m k & RN .W NH Q v F 1 J 1 k March 15, 1938. E. G. ROEHM 2,111,332

MULTIPLE AUTOMATIC PATTERN CONTROLLED MILLING MACHINE Filed April 23, 1937 I ll Sheets-Sheet 5 ZNVENTOR.

ATTORNEY.

March 15, 193-8. E. G. ROEHM 2,111,332

MULTIPLE AUTOMATIC PATTERN CONTROLLED MILLING MACHINE Filed April 25, 1937 11 Sheets-Sheet 4 r d w w m a; INVENTOR.

14.? 740 M 7 fiPlJ/A ,4 0f/7/"7 BY 12 77 {a ATTORNEY.

March 15, 1938. ROEHM 2,111,332

MULTIPLE AUTOMATIC PATTERN CONTROLLED MILLING MACHINE Filed April 23, 1957 ll Sheets-Sheet 5 7 1!; i Q 12/ l m 42; 124- ;z; u (594/ ms 1 424 3 :57 134 i I if! m 1o 359 i 360 11 358 if :5,; 127 45 INVENTOR ffiw/ famfl ATTORNEY.

March 15, 1938. E. G. ROEHM 2,111,332

MULTIPLE AUTQMATIC PATTERN CQNTROLLED MILLING MACHINE Filed April 25, 1957 11 Sheets-Sheet e INVENTOR. id/M 6 fox/W A VI/AQW/ll/i BY I I [:3 7 7 ATTORNEY.

March 15, 1938. ROEHM 2,111,332

MULTIPLE AUTOMATIC PATTERN CONTROLLED MILLING MACHINE Filed April 25, 1937 i1 Sheets-Sheet 7 w 1;] 2, 5 JZZQQ H7 I 73? H0 F I24 (9 15 7/ ATTORNEY.

March 15, 1938. ROEHM 2,111,332

MULTIPLE AUTOMATIC PATTERN CONTROLLED MILLING MACHINE Filed April 23, 1937 ll SheetsSheet 8 J; L; is? A is;

/ 19 0; g f /l V/A A A m,

INVENTOR. 5%) 6 foifl/v ATTORNEY.

E. G. ROEHM March 15, 1938.

MULTIPLE AUTOMATIC PATTERN CONTROLLED MILLING MACHINE Filed April 25, 1957 ll Sheets-Sheet 9 March 15, 1938. E. G. ROEHM 2,111,332

MULTIPLE AUTOMATIC PATTERN CONTROLLED MILLING MACHINE Filed April 23, 1957 ll Sheets-Sheet 10 ATTORNEY.

Patented Mar. 15, 1838 MULTIPLE AUTOMATIC PATTERN CON- MILLIN MACHINE TBOLLED lrwinG.Boehm,Norwood,0hlo,allignorto11ie Cincinnati Milling Machine Company, natl, Ohio, a corporation of Ohio Application April t8, 1'87. Serial No. 188.889

89 Galina.

This invention relates to die sinking machines, and more particularly to an automatic multiple pattern-controlled machine tool.

Certain industries depend almost entirely upon a diesforimpartingtheshapeorconfiguration to their articles of manufacture, and this is especially true in the bottle-making industry. Such dies are usually made in two halves, which are assembled for casting purposes; and

it) subsequently separated to remove the cast article. It will be apparent that the halves of the die will have a cavity of semi-cylindrical shape for the manufacture of ordinary round bottles; and various other shapes for odd shaped bottles,

which may be generally classified as quasi semicylindrical.

If these cavities had sufliclent size, a cutting tool could be mounted for swinging movement about a center lying in the parting line of the mold. This would permit the best cutting action because it is recognised that an end mill or and cutting tool operates most satisfactorily when maintained perpendicular to a tangent to the surface at' the point of contact with the tool. In

as the type of dies under consideration, it is rarely possible to mount the tool in this relation to the mold on account of the smallness of the cavities.

One of the objects oi this invention is to pro- ;10 vide a machine of the character described in which the cutting tool and the mold are so supported and manipulated during the progress of the cutting operation that a better cutting angle between the tool and the work is maintained 35 throughout the operation than has been possible in prior machines.

Another difliculty in the formation of the particular dies or molds under consideration is when the feeding cut is being taken longitudinally 40 of the mold, and the index ieed effected in a cross-sectional plane, that due to the acute angular relationship between the axis of the cutter and the tangent to the surface at the point of contact with the cutter, said tangent 5 lying in a cross-sectional Plane, a uniform angular index to the mold will not produce a uniform indexing movement between the cutter and the work as measured along the surface being produced.

so It is one of the objects of this invention to provide a novel and improved indexing mechanism which will produce a substantially uniform length of indexing movement as measured along the surface being produced, regardless of its shape,

55 or the angular relationship 01' the cutter axis to Oincin the tangent at the point of contact with the surface.

It is another object of this invention to provide a machine of the character described in which the work and tool are mounted on swinging sup- 5 ports rather than sliding supports, and in such a balanced manner that a minimum of power is required to manipulate them during the cutting operation.

invention should be readily apparent by reference to the following specification considered in conjunction with the accompanying drawings illustrative of one embodiment thereof, but it will be understood that any modifications may be made in the specific structural details within the scope of the appended claims without departing from or exceeding the spirit of the invention.

Referring to the drawings in which like reference numerals indicate like or similar parts:

Figure l is a perspective view of a machine embodying the principles of this invention, having partially broken-away parts to bring out certain features of the operating mechanism.

Figure 2 is a front view of a portion of the machine shown in Figure 1 with certain parts broken away, and other parts in cross-section.

Figure 315 a cross-section through the machine asviewed on the line 3-3 of Figure 2.

Figure 4 is a cross-section through the reservoir tank.

Figure 5 is a section through the machine showing a cutter support and work support unit in elevation, as viewed on the line H of Figure 2.

Figure 6 is a section through the pattern support unit as viewed on the line 6-,4 of Figure 2. m

Figure 7 is a detail section taken on the line 1-1 of Figure 8.

Figure 8 is a vertical cross-section through the tracer support unit shown in Figure 3.

Figure 9 is a cross-section through the pattern 5' 2 supporthousingssviewedonthelineHof Flgure2.

Figure 10 is a section through the pattern support housing as viewed on the'line ll-il of Figure 6, showing the indexing drive mechanism.

Figure 11 is asection through the valve block as viewed on the line il--li of Figure 3.

Figure 12 is a detail view of the ratchet mechanism as viewed on line I2--i2 of Figure 2.

Figure 13 is a section on the line iI-il of Figure 2 showing the index drive mechanism to the work support.

Figure 14 is an enlarged view of the variable index feed control mechanism.

Figure 15 is a detail section on the line il-ll of Figure 14.

Figure 16 is a section through the reversing valve for the indexing cylinder as viewed on the line Itll of Figure 2.

Figure 17 is a horizontal section through the work holder unit.

Figure 18 is a detail section on the line 18-" of Figure 7.

Figure 19 is a diagrammatic view of the hydraulic control circuit.

Figure 20 is an enlarged detail view of the trip control mechanism associated with the pattern support.

Figure 21 is a section on the line 2i-2i of Figure 20.

Figure 22 is a section on the line 22-22 of Figure 20.

Figure 23 is a diagram for use in explainingthe principle of indexing.

Figure 24 is an enlarged detail sectionas viewed on the line 2|--2l of Figure 3.

Figure 25 is a section through the valve block as viewed on the line 28-25 of Figure 3.

Figure 26 is a section on the line 26--2l of Figure 24.

Figure 2'7 is an enlarged detail of portions of the tracer support.

Figure 28 is a section through one of the cutter carriers showing a low speed cutter spindle unit substituted for a high ,speed spindle unit.

Figure 29 is a-section on the line 20-28 of Fi ure 28.

Referring to Figure l of the drawings, the reference numeral 25 indicates the base or main support of the machine which has a predetermined width, but may be made of any suitable length depending upon the number of cutting units to be mounted thereon. This machine is a multiple die-sinking machine, and to that end there is mounted upon the support, a central unit 28, which may be termed the control unit, because it includes the pattern and tracer; the feeding mechanism which is automatically controlled by the tracer; and the indexing mechanism by means of which the tool and work are relatively indexed after. each cutting stroke. Mounted on opposite sides of the. control unit are a plurality of cutting units 21, 28, 2s, and 30. For illustrative purposes there is shown two cutting units on each side of the central control unit, but this number may be increased or decreased -as desired, or the cutting units may be mounted all on one side or the other of the control unit, without departing in any way from the principles of this invention.

Referring to Figure 3, the control unit 26 consists of a column II which is fixed with the bed 25, for pivotally supporting on one vertical face a tracer control unit 22. This unit is trunnioned at 23 to the column, and actuated by a link It which ispivotaily connected at II to ingunitandstlltoacrankl'liisedonsnosciliatable shaft a. The crank 21 has an arm 2| which is pivotally connected at 0 to a piston rod ll. The piston rod passesthrough one end of a cylinder 42, for attachment to a piston 42. The cylinder 42 is trunnioned to'swing about a pivot II, It will now be evident that admission of fluid pressure to the right hand end of cylinder 42 will cause counterclockwise rotation of the crank 81 and a downward swinging movement of the tracer unit 22; while admission of fluid pressure to the other end of the cylinder will cause a reverse direction of movement of the connected p'arts.

In this machine the cutting is performed during the upward swinging. movement of the tracer and connected cutters, and therefore fluid pressure is forced into the left end of cylinder 42 to sheet the feeding or cutting stroke, and after separation of the work from the cutters, fluid is forced into the right hand end of cylinder 42 to eifect a rapid traverse downward movement.

The pattern which cooperates with the tracer is supported in a swinging carrier 45 which is trunnioned at 48 to the bed 2! for movement toward and from the tracer support. It will be noted that the dead weight of this carrier is carried at all times by the bed 25, and that it stands in substantially a perpendicular position so that very little effort is necessary to swing the carrier toward and from the tracer unit. As shown in Figure 2, the carrier 45 has an upwardly extending lug 41 upon the sides of which are formed guide surfaces It and 49 which are in contact with guide surfaces 50 and Si formed in a bracket 52 which overhangs from the column 8i. This guiding means insures against any side sway or weaving of the carrier during the "in and out" movement.

The carrier ll is oscillated toward and from the tracer unit by means of a link 53 which is pivotally connected at 54 to the carrier, and at I! to a crank II which is integrally secured to a longitudinally extending oscillatable shaft 51. The crank 58 has a pivotal connection at 58 with piston rod 50, to the end of which is attached the piston l0, which is contained in the cylinder ii.

The cylinder ll is 'trunnioned at 62 on the back of the column II, for free oscillation in accordance with the movement of the pivot 58 about the shaft II. It will now be evident that ii pressure is admitted to the lower end of cylinder ii that the pattern support 45 will move away from the tracer support, and that if pressure is admitted to the upper end of the cylinder, the pattern support will move toward the tracer support. For thepurposes of description, the movement of the pattern carrier 45 will be referred to as the "in and on movement.

Referring to Figure 5, each cutting unit' consists of a column member 3|, which is similar to. that shown in Figure 3, for supporting upon one vertical face a bracket 63 which is trunnloned at N. This bracket is connected by a link 85 to a crank Bl integral with the shaft 38. A cutter spindle 61 is journaled in a quill 68 carried by the bracket 68, and the other end of the spindle projects beyond its bearing so that it may be provided with a pulley 88'.

- This pulley is connected by a belt 89' or other motion transmitting band, to a two step pulley 69 secured to-the armature shaft of an electric 'motor II". It will be noted that the motor is It will he noted shaft as that shown in l igure 3, extends longitudinally for the full length of the machine, so that all of the cutter spindle brackets may be operatively connected thereto tor simultaneous actuation thereby. Thereiore the hydraulic motor consisting of the piston and cylinder 4! and II common motor for electing a of all of the cutter spindles.

Bach cutting unit also includes a swinging carrier II, in which is mounted a work support and this carrier is supported and operated in the same manner, as the carrier 4| shown in figure 3. In other words the carrier II is pivoted at H to the bed II and guided at 12 in an overhanging bracket 13 projecting from the column Ii. This carrier is also connected by a link I! to a crank arm 13 which is integral with the shaft '1. As seen in Figure l, the shaft ll extends longitudinally throughout the length of the machine and serves as a common actuator for moving the work supporting carriers toward and from the cutting tools.

Tracer control mechanism The tracer control mechanism is more particularly shown in Figures 8 and 27 of the drawings, in which the reference numeral 14 indicates the tracer head which, as more particularly shown in Figure 3, is secured to the tracer control unit 32. This head has a tubular opening II in which is fitted a sleeve 1|, the sleeve having a threaded portion l'l adapted to interengage threads 18 which are out on the interior of the housing. The sleeve 18 supports the tracer arm II for universal movement in the following manner. The tracer arm has an enlarged portion 8. which serves to form a shoulder Ii. Against this shoulder there is placed a thin metal diaphragm 82, and against that is placed a metal disc ll, which has a boss ll formed integral with one side, which serves as a separator between the disc and the diaphragm. A nut II is threaded on the tracer arm I! and serves to clamp these parts against the shoulder II. A ring 86 surrounds the disc and diaphragm and this ring has an internal annular projection II which is of the proper thickness to fit between the opposing faces of the diaphragm and disc and act as a illlenblock and also as a support against which the diaphragm may be clamped. The ring 88 has a face I! which abuts against the end of the sleeve II andthis face is so spaced from the shoulder ll that a clearance space 80 is provided between the opposing faces of the disc and the end of the sleeve 10. The parts so far described may be assembled upon the tracer arm I9 and then insertedin the end of the sleeve ll after which they may be clamped in place by the member SI which is dish shaped so as to provide a narrow annular face which will engage the periphery of the diaphragm l2 and clamp it against the ring 86. The clamping bolts 92 pass through clearance holes in the disc and diaphragm and are threaded in the end of the sleeve 18. .From this it will be seen that the tracer arm ll is supported by the diaphragm It. When the tracer is deflected, some point on the periphery of the disc 8! acts as a fulcrum shown'inl igure3.constitutesa' l a bill III.

in engagement with the end of member III by a means of a spring Ill.

The valve member II! has a central or neutral position in which during the cutting stroke, it holds the piston ll against movement; a second position to one side of this neutral position in which it causes movement of piston l. in one direction; and a third position on the other side of said neutral position in which it causes movement of piston II in an opposite direction. By

'means oi this arrangement it is possible for the tracer to control the "in and out" movement of the pattern and work supports automatically during the cutting stroke.

It is desirable, of course, that when the tracer is out of contact with the pattern, that the valve plunger I" be in such a position that it will cause the pattern and work supports to move toward the tracer and cutters.

Therefore the spring ill should be sufliciently strong to urge the valve ill and deflect the diaphragms l3 and 8! to the left as viewed in Figure 8. a sumcient amount so. that the valve I" will cause a flow of fluid to the cylinder Si in such a manner that the piston 6| will cause the correct direction oi. movement of the connected supports. 'lhis will make it possible when the tracer engages the pattern for the pattern to move the tracer arm to the right, as viewed in Figure 8, a suiilcient amount to take the deflection out of the diaphragms'and move the valve ill! to a central position. From this it will be apparent that upon assembly of this tracer mechanism, the connecting arm II! should be of such length that when the diaphragms I! and II are undeflected, that the valve Ill! will be in its central or neutral position.

The tracer control valve consists of a valve body I I! in which is formed abore illi. Mounted in this bore are a plurality of discs lil'l of varying thickness,.some of which are provided with annular shoulders on the end face or faces, and radial slots, so that when they are all assembled in the bore I08 they serve to form flve annular grooves or ports ill, in, III, III and H2. The valve plunger I03 has a first annular groove III which is of such length that when the valve is in a neutral position it will only extend to the edge of ports ill and H0 so that both of these ports are closed with respect to port ill; and a "Yin eitherdiiootion from its neutral 'wlllrestrictthefiowfrcmport III toport Ill,

seoondannularsrcovelllwhiehisofnehlength that it interconnect. port III with port III wherebyupcninovementofthe-valveplungerlll Podium it byclosingoneortheotherof theseports dependent upon the direction of movement.

Since this machine is a precision machine, a precaution is taken against ilne particles of dirt or other foreign matter impeding free movement of the valve. by providing means for constantly rotating the valve. This also aids in preventing the valve from sticking due to inequality in the lateral pressures on the valve at the various points opposite the diiferent ports. By continuously rotating the valve. a thin film of oil around the valveisassuredwhlch actsasaiubricant toprevent sticking. The valve rotating means consists of a small fractional horse power electric motor III which is supported on a frame III secured to the end of the valve body Ill. and within this frame is antifrictionslly iournaled. a worm wheel I", which is driven by aworm Ill secured to the end of the armature shaft of the motcr.

The worm wheel is supported in axial alignment with the valve plunger III, and is mounted on a sleeve III which has an enlarged head III. The valve plunger III has a diaphragm III secured to the end of it, and this diaphragm has a pair of diametrically opposed ears which engage in slots formed on a flanged portion of the head I whereby rotation of the head will cause rotation of the valve without interfering with its longitudinal movement. The spring Ill previously referred to, is supported within the sleeve lit, and a suitable member III is interposed between the end of the spring and the valve, to transmit the pressure thereto. An adlusting screw I23 is threaded in the end of sleeve I II to vary the tension of spring Ill.

Pattern and work supports The pattern and the work are supported in fixtures which are identical in construction and therefore a description of one will sumce for all. Referring to Figures 3, 8, '7, 9 and 17, the fixture itself comprises a rectangular frame I which, as shown in Figure 6, is provided at the top with a rectangular guide surface I26 and at the bottom with a guideway I25. This permits movement of the frame relative to its supporting cradle I21 which has a top trunnion I28 and a bottom trunnion I28 whereby the cradle may swing relative to the frame. By mounting the cradle I21 for oscillation about its trunnions "8-128 makes it possible to index the pattern and work after each cutting stroke.

The rectangular frame I is provided with a pair of vertically extending T-slots Illl, Figure 9, by means of which a pair of cross bar supports Ill and I3! may be secured in various vertically adjusted positions on the frame. The lower cross bar I3I has a horizontal surface In upon which the pattern or work, represented by the dot-and-dash line I, is supported; a pair of vertical surfaces I" against which the mold is clamped to lock it relative to the axis I" about which the cradle swings; and a second pair of vertical dove-tail surfaces II! which engage the sides of the mold to prevent spreading thereof when the same is clamped.

The top cross bar III is provided with a vertical surface I against which the face of the mold is clamped and a plurality of adjustable set screwslilfor nsegingthetopofthemoidand preventingthelamefromliftingduringtheeut.

Themoldisclampedinpositionby meansoi'a cllmpinslcrew Ill whichisthreadedthrougha u-shapedbracketlllwhicnasshowninligure 17, has ears I at each end which project into vertically extending rectangular slots in formed in the frame I. In order to hold the bracket III in any given vertical position. the bracket III is Provided with which is threaded a set screw III, as more particularly shown in Figure 'I. This set screw tends to shift the bracket III laterally of the frame III and thereby hold it in the position by wedgins the same between the sides of the frame I24. It will be apparent that the specific details of the fixture may be varied in accordance with the size and shape of the molds to be reproduced, but in principle the fixtures provide a vertical locating surface against which the parting face of the mold may be clamped and means in back of the mold for clamping and holding the mold against this locating surface together with means to prevent the face of the mold from separating due to the fact that the mold is somewhat semi-cylindrical in shape and the clamping force applied to the mold is in such a direction and in such a position that it might cause a certain amount of spreading.

The hydraulic tracer control circuit- This machine is hydraulically operated and in Figure 19 there is shown a diagram of the complete hydraulic circuit. In this circuit there is shown a stop valve I", a stop valve operating plunger I", anin and out" control valve ill, a longitudinal control valve I48, and an index control valve IN. All of these valves are in a position corresponding to rapid traverse movement of the cutter and tracer downward to a starting position. During this movement all of the various carriers are moved out so that the work pieces are out of engagementswith their respective cutters and the pattern is out of engagement with the tracer. This means that the tracer control valve plunger I03 is shifted to the left of its neutral position as viewed in Figure 19 by the spring Ill. During-this rapid traverse movement, the piston 80 which controls the in and out" movement of the carriers remains stationary, and the piston ll moves rapidly toward the left as viewed in Figures 3 and 19 to thereby move the tracer and cutter downward to a Since the same unit pressure of the pump is acting on both ends of piston 43, and since one end is larger in area than the other, the piston 43 will move to the left as viewed in Figure 19, whereby the fluid in the left end of cylinder 42 will be returning through channel I59 to port I58 of the stop valve. In other words, there will be an incoming flow through ports I51 and I I! which will combine in the annular groove I60 formed in the stop valve plunger I46. This combined flow will continue through channel IBI to port III of the "in andout" control valve I.

This valve has a plunger I", in which is an upstanding lug iel'throughformed an annular groove I84, which, in the)- sition shown, connects port I82 to port I85. This port is connected by channel I88 to port I81 oi the "longitudinal control valve I48. In the position of the plunger I88 of this valve, an annular groove I88 connects port I81 to port I18. The port I18 is connected by channel "I to the right hand end of cylinder 42. It will now be seen that the flow from pump III and the flow from the left end of cylinder 42 is combined in the stop valve, and will flow through the interconnections Just mentioned to the right hand end of cylinder 42. I

This flow is further increased by the rapid traverse pump I52, having an intake I12, through which fluid is withdrawn from reservoir I55 through a strainer I13, and a delivery channel I14, which leads to port I15 of the longitudinal control valve I48. At this time the port I15 is connected by annular groove I18 to port I11, which in turn is connected by channel I18 to port I18 01' the in and out" control valve I48. The plunger I83 has a second annular groove I88 which is of suflicient length that the port I18 is interconnected with the port I85.

It will be noted that it was through this port that the combined flow from pump II and the out control valve I48, has a branch line I8I to which is connected the deliverychannel I82 of the "in and ou supply pump I83. This pump also has an intake I84 for withdrawing fluid through a strainer I85 from the reservoir I55. The channel I8I terminates at the port I82 formed in one end of the "in and out cylinder 8|. This-will not cause movement of the contained piston, however, because the other port I83 of this cylinder is connected by channel I84 to interconnected ports I85 and I88, and channel I81 to port I88 of the in and out" control valve I83, which port is closed at this time by the spool I88 on the plunger I83.

Since the delivery from pump I83 cannot cause any displacement of the piston 88 in the cylinder 8|, the practical result will be that the delivery from this pump will pass through channel III and combine with the delivery from the rapid traverse pump, which is now flowing through channel I18 and to which channel the line I8I is connected. From this it will be seen that all three pumps I5I, I83, and I52 combine to cause be escaping therethrough. It is possible, however, to connect the port I8I in case of emergency to the stop valve operating plunger I41. In other words, during this rapid traverse movement, if the tracer should hit a foreign obstruction and thereby shift the valve I88 to the right, the port "I will be connected to port I88 and fluid will then flow through channel I88, interconnected ports I84 and III of the double throttle valve I88, channel I81, annular groove I88 of the in and out" valve I48 which is connected by channel I88 to port 288 of the index 'control valve I88.

At this time the port 288 is connected by an annular groove 28I formed in plunger 282 of this valve to port 288. A channel 284 connects this port to port 285 of the "in and ou" control valve I82. Plunger I83 01' this valve has an anw nular groove 288 which interconnects ports 285 to port 281 so that the fluid continues to flow through channel 288 into the right hand end of cylinder 288 in which is slidably mounted the plunger I41. When this happens, the plunger I41 is shifted to the left against the resistance of spring 2I8 and thereby actuates, through the crank 2| I, the stop valve plunger I48, and shifts the same to the right thereby closing port I58, and preventing the escape of fluid from the left end of cylinder 42. This will act as a sort of cushioned stop to the movement and if a high pressure builds up in the delivery channels of the various pumps, the emergency relief valves 2I2, 2I3, and 2I4 associated with the respective pumps will open.

At the end of the rapid traverse movement, a trip dog 2I5, which is shown in Figure 3 as securedto a T-slot 2I8 formed in a depending bracket 2I1 of the tracer support 32, actuates a trip lever 2I8. This lever is pivotally supported at 2I8 by the column, and has an integral crank 228 which is connected by a link 22I to a crank 222 secured to the lower end of rod 223. As more particularly shown in Figures 11 and 25, a crank arm 224 secured to the upper end of this rod engages an upstanding lug 225 formed on a valve shifter 228 which is supported for free rotation relative to the shaft 223. It will be noted that there is a certain amount of lost motion to be taken up before the crank 224 engages the lug 225. When this lost motion is taken up the shifter 228 is rotated a sufflcient amount to cause the spring pressed detent 221 to rideover the peak 228 formed on a notched plate 228 integral with the shifter whereupon a spring 238 will cause the detent lever 221 to complete the movement of the shifter. This constitutes a form of loadand-flre mechanism for actuating the shifter member 228.

Referring to Figure 25, it will be noted that the shifter 228 is provided with two actuating arms 23I and 232, the former of which has a pin 233 interfitting in a notch formed in the end of the index valve plunger 282 and the latter having a pin 234 interfltting in a notch formed in the end of the longitudinal" valve plunger I88. Therefore when the trip lever 2I8 is thrown by the "dog 2I5, both the longitudina valve plunger and the index valve plunger are shifted to the left, as viewed in Figure 19. The effect of this is to stop the rapid traverse movement of the cutters and tracer, initiate an indexing movement of the work and pattern, and also to initiate an inward movement of the pattern and work toward the tracer and cutters. This is brought about in the following manner.

When the valve plunger I88 is shifted into its left hand position, it establishes three new connections. First, it interconnects port I15 with port 235 whereby the rapid traverse pump is disconnected from the actuating cylinders and connected to the reservoir line 238. This disconnects the rapid traverse pump from the entire with port 231.

By means of channel 2 39, the port 291 is connected to port 299 of the double throttle valve I99. A tapered spool 249 formed on the plunger 2 of this valve, serves to interconnect port 299 with port 2, which in turn is connected by channel 2 to port I ofa secondary control valve 2". 1

The secondaryv control valve has a pressure port I which is connected through an hydraulic resistance 241 and branch line I to the delivery channel I" of pump Iil. It will be noted that the pump Iii is connected directly to one end of cylinder 42 and through the hydraulic resistances 2" and tapered spool 2", which also causes a drop in pressure, to the other end of cylinder l2. The'hydraulic resistances 2i] and Il cause a sufficient drop in pressure in the fluid supplied to the large end of piston 9, that the total resultant. pressure on the large end of the piston is equal to the total resultant pressure on the other end, whereby no movement of the piston takes place and therefore the downward movement of the tracer and cutters must stop.

The third or last connection effected by plunger I89 is the intercoupling of port I95 with port I99, whereby one end of cylinder BI is coupled to reservoir. This is true because the line I91 leading fromport I9! is connected to port I95 of the double throttle valve I96, and due to the position of the tapered spool 250, port I9! is interconnected with port I94. As previously described, this port is connected by channel I93 to port ,III9 of the tracer valve, and since the tracer valve at this time is in its left hand position, the port III! is interconnected to port I" which leads to reservoir. Since the other end of the cylinder BI is directly connected through channels |9I and Ill to pump I83, the piston ill will be moved rapidly in a direction to swing the carriers 45 and II in toward the cutters and tracer.

The index valve IIII has a pressure port "I I which is supplied from a separate pump 252 through channel ill. when the index valve plunger 29! is shifted to the left as previously mentioned, it interconnects the port III with port "2 whereby the fluid will flow through I channel 259, feed-stop valve Ill, and channel 255 I in this figure actuates a trip lever 294 and there-- to port iii of cylinder 2". A piston 259 contained in the cylinder actuates an indexing mechanism (the speciflc' construction of which will be described later), which in turn will index the work and pattern a predetermined amount so that a new portion of the work will be presented to the. cutters on the next cuttingstrolre. The fluid escaping from the. other end of cylinder 251 will pass through channel 259, feed-stop valve 254, channel 290, port "I of the index valve, which is now connected to port- 292, and then to the return line I". I

It will now be apparent that the downward movement of the cutters and tracer has been stopped, the indexing. movement has been ei- Iected, and the carriers 45 and III are swinging inward toward the cutters and tracer.

' Shortly after this inward movement starts, an elongated dog 269, Figure 20. mounted on the carrier" and moving toward the right as viewed thereto and sequen umac by causes rotation of lever arm Ill, 22.

This lever arm is connected by a long link. 291

to a lever arm Ill, Figure 3, keyed to the upper end of a vertical shaft 299. This shaft. as'shown in Figure 11, has a short lever arm 219 secured a s s s ms: 2'" and 212 integral with detent plate I'll. It will be noted that there is a certain amount of lost motion between the lever. 210 and the lugs, whereby upon rotation of the lever arm in either direction, the spring pressed detent I" will be caused to ride over the peak ill formed in the detent plate and thereafter automatically complete the movement. This mechanism constitutes a loadand-fire mechanism for actuating the in and out" valve similar to the one described for actuating the longitudinal control valve.

The detent plate 219 hasa pin 218 which engages a notch formed in the end of the "in and on plunger I93 automatically shifting the same. When the dog 263 actuates the trip lever 264 as just described, it causes rotation of the detent plate 219 in a clockwise direction as viewed in Figure 11, and thereby shifts the valve plunger I63 to the left as viewed in Figure 19.

In this new position of the valve plunger I99, the ports I65 and I92 are disconnected i'rom one another, and the port I19 is interconnected with port I88. No result follows at the present time because the port I99 of the "longitudinal" valve to which the port I99 is connected by channel I91, is closed and therefore this becomes a dead line for the present.

During this movement of the tracer valve plungenit will be apparent that the reservoir port III! will gradually be closed so that the channel I93 through which the exhaust fluid from the large end of cylinder BI is flowing to reservoir will be blocked and when the port Illl is completely closed, the inward movement of the tracer and cutters will be stopped. During this same time the port III is gradually being opened to thereby connect the pressure port III to channel 219. The channel 219 is connected to the left end of cylinder 245 whereby the pressure from pump I83 acts directly on the end of the contained plunger 299 and tendsto shift the same toward the right. The movement is restrained by a flexible diaphragm 28L The movement, however, is sumcient to connect port 292 which, up to this time, has remained closed, with port I".

The port 2 is connected at this time, as previously described, with the right hand end of cylinder 42 and since the other end of the cylinder is under pressure from pump I5I, this connection permits the fluid from the right hand end of cylinder 2 to return to reservoir through channel!" which results in an upward feeding movement of the tracer and cutters. It will be apparent that .the rate of this movement will depend upon the amount that the port .292 is opened, which, in turn, will dependupon the amounts that the ports III and II! are opened, which is dependent upon the position of the tracer valve plunger Ill.

. The maximum amount of opening of the last named ports will correspond to the central position of the tracer valve plunger Ill, because movement to either side of this central position will now be apparent that the tracer is capable 7 .1- arm-,sss of controlling the rate of: the upward i'eeding r movemenhandthatwhenthetracermovesirom its central position in either direction it will decrease that rate of ieeding movement. In addition it willeause an inward or an outward movement of the carriers 4! and II, dependent upon whether the pressure port III is connected to channel III or whether the exhaust port ill is connected thereto.

Itwillbe notedthat theports ill and li2will causeadropinpressureinthe fluidiiowing to channel Ill, and thus they constitute a form of hydraulic resistance. with the result that. the channel I'll constitutes a form chamber-having a resistance "in" and a resistance out". If these resistances remain unchanged, a constant pressure will exist in the chamber. In other words, it the hydraulic resistance 2 were not provided, the pressure in channel 219 would eventually build up to the pressure in channel I" regardless oi' the resistance of ports ill and H2 and no control over the position of plunger 28!! would be possible.

At the end of the upward cutting stroke a trip dog Ill, shown in Figure 3, actuates the trip lever Ill, and thereby shifts the interconnected valve plungers' I68 and 202 to the right or in other words. into the position in which they are shown in Figure 19. This results in the interconnection of ports I86 and it! so that the pump I can now deliver fluid coming through channel I81 to port Ill of cylinder Ii, and since the pressure on the large end of piston 60 is now greater than the pressure on the small end, the carriers 45 and will immediately start to move outward. The rate of this movement will be rapid because the rapid traverse pump III is interconnected at the same time by the annular groove "8 in plunger I68 to channel I'll which thereby increases the volume of flow acting on the large end of piston 60.

The shifting of plunger I" to the right also disconnected the port "I from port 281, so that channel I'll which leads from the right hand and of cylinder 42 and through which exhaust fluid was passing to reservoir during the cutting stroke, is now connected to a dead line I88 whereby upward movement of the tracer and cutters stops.

Shifting of the index valve plunger 2" to the right interconnected pressure port Ill to port I which thereby caused fluid to flow to the lower end oi the index cylinder 2" resulting in a repositioning movement 01' the index mechanism preparatory to moving the pattern and work another small amount dependent upon the amount of material it is desired to remove on the next cutting stroke. The carriers continue their outward movement until a shoulder 286, Figure 21, formed on the dog 28!, engages shoulder 281 formed on the member 2. This member is pivotally connected by a pin I" to a rectangular portion 290 formed integral with the trip lever I. This results in the shalt 165 which supports these parts, being rotated to cause shifting of the in and ou valve plunger I" to the right or into the position shown in Figure 19.

The eitect of this is to stop the outward movement of the carriers by disconnecting port I from pressure I19 and also results in arapid traverse downward movement 01' the tracer and cutters. The circuit is now conditioned to repeat the cycle just described and the repetitions will continue until the work piece or pieces have been nnished.

In order thatthe work pieces may be readily removed, it is desirable that the carriers move further back from the tools than during the cutting operation. To this end on the last outward stroke of the carriers. the operator swings the member ill, Figures 20 and 21, by means oi the handle ill about the pivot 28! so as to.

remove the shoulder Ill from the path ofthe shoulder ill on dog I. These parts may thus pass one another. and the carrier will continue its outward movement until a second dog 29! attached to the carrier engages trip lever 283. To prevent interference, the dog 29! has an L- shaped projection 294 which extends to the other side of the T-slo't plate 295 so as to be in the plane of the trip lever 29!. This lever is supported for tree rotation on a shaft 296 and has an arm 281 engaging the bifurcated end I" of link 29!. A spring "ll continuously urges the link and arm 281 in a counter-clockwise direction and a pin "I is positioned to limit this movement.

As shown in Figures 3 and 26, the link 2" ex- 4 tends to a bracket 302 for operating a lever 303.

The lower end of this lever is partially cut away to form a projecting lug 3. The end oi the link I" is flattened and a portion of it cut away to form a shoulder 305 which is adapted to engage the lug 3M and cause rotation of the lever 30! in a counter-clockwise direction. Upon actuation of the trip lever 293 by the trip dog in a clockwise direction, the link 289 moves toward the right and swings the lever 30! and its supporting shaft 306 to which it is keyed in a counterclockwise direction. The lever llll extends above the shaft "8, Figure 24, and is connected by means of a pin Sill to a second lever 3" supported for tree rotation on the shaft 306 and the lower end of this lever is pivotally connected to the bifurcated end of link 309. This link is connected by a crank Bill to vertical shalt 3| I, which shaft,

as shown in Figure 11, has integrally connected thereto a lever 3|! which has a wide notch Ill cut in the end thereof. This notch is suillclently wide to provide a lost motion connection with a pin 3 fixed in the detent plate iii.

This plate has two V-shaped notches lit and ill cut in the edge thereof but of diilerent depth so that the intervening peak Ill is unequally spaced with respect to the bottom oi the notches. The reason for this is that it is desirable that a small rotative movement be given to the parts in order to shift the stop valve to its stop position. Since this valve is also used for emergency stops by means oi a manual control lever, it reduces the length of movement that must be given to the lever, and makes it possible for the operator to very quickly stop the machine in case of emergency. A spring pressed detent 3|! is provided for automatically completing the movement whereby the mechanism acts as a load-and-i'ire mechanism.

The pin Ill, whichis integral with the plate iii, projects through the other side of the plate into a slot formed in the end of the stop valve plunger Ill for shifting the same. It will be noted that the lever arm 2 which is actuated by the hydraulically actuated stop plunger I", is integral with the plate 3|! and that the pin 32! mounted in theendof the lever II I has a lost from the hydraulically actuated stop plunger I".

For manual operation, a hand lever 222 is secured to the shaft ill, and the lower end of this leverhas a pair of spaced projecting lugs "land 224. These lugs are positioned to engage opposite sides of the lug. 804 which prolects from the lever 202. The wide spacing permits the link 2|! to throw the lever 20 without interference from the lever 322. The shaft Ill extends the full length of the machine, as shown in Figure 2, and

is provided with additional operating levers, such as the one, 304, shown in Figure 5, whereby the operator may stop the machine from any one of a number of stations about the machine. In other words, upon rotation of the shaft "I by any of these stop levers, the lug 324 on the lever 322 will be moved into engagement with the lug 304 on the lever 303 and rotate the latter in a direction to cause shifting of the stop lever to its stop position. Upon rotation of the lever 222 in an opposite direction, the lug 222 will shift the lever 303 in an opposite direction and move the stop valve to a starting position. Thus the machine can be automatically stopped by the trip dog 292, but can be started only by manual actu ation of the lever 303.

Indexing mechanism As previously mentioned, a constant angle of indexing will not produce a uniform cross feed as measured along the surface of the work due to variations in the length of the radii of the various points on the periphery of non-circular bottles. .This is obviously true because the opposite side of an angle increases in length with increases in length of the hypotenuse and in spite of the fact that the proportion between the side and the hypotenuse remains the same. Therefore, the longer the radius, the greater will be the length of the cross feed for the same angle of index. For practical reasons, in this machine it is desirable that the length of each indexing movement or cross feed as measured along the surface of the work be substantially uniform, which means that the opposite side of the angle must be kept uniform. and this can only be done by changing the size of the angle in accordance with changes in the length of the radius.

For purposes of explanation, an assumed standard length of cross feed may be arbitrarily chosen and by also choosing a standard length of radius, it can readily be determined through what angle the radius must be moved to produce the arbitrarily chosen length of feed. For convenience, this radius may be equal to the average of the longest and shortest radii which can be produced in the machine. For example, referring to Figure 23, let R equal the length of the longest radius, and r the length of the shortest radius, then the length of the average radius In this figure, the line as may be assumed to represent the outline of the surface to be cut in a mold; the line 821 to represent the parting line of the mold; and the center 22. to represent the axis about which the mold is indexed. The assumed standard distance of index feed is represented by the numeral 329 as measured along the circle as, and from this it will be apparent that the radius R, or in other words the mold, must be rotated through an angle indicated by the reference numeral "I in order to eflect this unit feed distance. If the outline of the mold was a aliases true circle, as represented by the line), it is apparent that the angle Ill could remainthe same throughout the entire machining operation and a uniform feeding movement would be effected at each indeflng. In other words, an operating plunger could be geared to the work support-and,taking into consideration the ratio of the connecting. gearing, it could be very readily determined what the length of stroke of the plunger should be to eflect this unit index angle.

Fbr irregular shaped bottles,'such as represented by the outline 82!, this procedure will not apply because the angle of index must be varied in accordance with the length of the radius of the point of the surface being worked upon. This angle can be varied by varying the stroke of the plunger, and mechanism has been provided whereby this is automatically effected for each indexing movement. To this end, an outline control cam 222 is provided as shown in Figure 14, which is keyed to a shaft 323 anti-frictionally .journaled in the carrier II and connected by bevel gearing I, Figure 6, to a tubular shaft I. This shaft is anti-frictionally journaled in the carrier ll and carries a base plate at forming part of the swinging frame I21. The lower end of this shaft is connected by a worm gear 231 and a worm "I to a shaft Ill which extends the full length of the machine and provided with similar worms for actuating worm gears connected to the individual operating shafts, which rotate the various work holders, as shown in Figure 3.

The shaft 320 has a gear couplet fixed thereto comprising the spur gears 34! and I which may be selectively interchanged by spur gears "2 and 242 respectively slidably mounted on a spline shaft 2. The shaft 2 is connected by change gears Ill and I to a second shaft 241 which is mounted in the carrier ll in parallel relation with shaft 3.

Referring to Figure 15, these parts are actuated by a piston 25! which is slidably mounted in cylinder 2", previously referred to in the description of the hydraulic circuit shown on Fig ure 19. The piston rod 3, which is connected to the piston 28!, has rack teeth 2 formed on one side which interengage with a pinion "I. The piston rod also has connected thereto a projecting lug "I which is adapted to engage the periphery of a stop cam I52.

The pinion 350 is moimted for free rotation on shaft I" which is journaled in the carrier frame. The pinion I" has integrally formed therewith a ratchet wheel I" which, as shown in Figure 12, will be rotated in a counter-clockwise direction upon downward movement of the plunger "I. A pawl carrying plate III is keyed to the shaft 3" in adjacent relation to the ratchet wheel and is provided with four pawls 2" which are pivotally attached to the plate and held into engagement with the ratchet teeth by means of spring pressed plungers Ill. It will be noted that the teeth point in such a direction that upon counterclockwise rotation of the ratchet wheel. it will engage :ne of the pawls and cause rotation of the plate 2" and connected shaft 241 in the same direction, and that upon clockwise rotation, the ratchet teeth will ride under the pawls without causing rotation of the plate,

As shown in Figure 10, the plate 2 has integrally connected therewith a second ratchet wheel 2", the teeth of which point in an opposite direction to those on the ratchet wheel 3". A second pawl carrying plate I" is mounted in amass adjacent relation to this M named ratchet wheel, but thisplate is held against rotation W a pin are, as more particularly shown in ligin'e 6. Theresultisthatduringtheciockwisereturn motion of the ratchet wheel "8, the pawls I on plate III will engage the teeth on ratchet wheel Ill and prevent any return movement of shaft 841 during the upward or ratcheting moveshifted on the ment of actuating plunger Ill.

The gear couplet "IA" is spline shait I by a shifter fork Ill which is slidably mounted on a supporting spline shaft III. An operating shaft "3. which is actuated by the handle 8, shown in Figure 2. has an eccentric pin "I on the end which engages a slot ill formed in the shifter fork in such relation that the handle "I may assume three diflerent positions, in one of which the gear 843 is in mesh with the gear Ill; in a second of which the gears are disengaged or in a neutral position; and in a third of which the gear m is in mesh with the gear 8.

The neutral position which has been provided makes it possible to rotate the shaft are manually to return the pattern and work holders to a starting position without interfering with the previously described ratchet mechanism. This manually operable means includes a sprocket wheel I" which is keyed to the shaft "I. This sprocket wheel is connected by a chain "I, Figures 2 and 3, to a second sprocket wheel "I ilxed on shaft 310. This shaft is connected by bevel gearing ill to a shaft 812, which projects from the carrier and is provided with an operating hand wheel 31!. It will now be apparent that rotation of the hand wheel will cause rotation of shaft 33! and thereby rotary movement of the pattern and work carriers.

The mechanism shown in Figure 10 constitutes the connecting gearing previously referred to between the operating plunger 3" and the indexible supports. The length of the stroke of the plunger 8 is determined by the position of the stop cam ll! during the upward or ratcheting movement of the plunger. In other words, iluid is admitted to the lower end of the index cylinder 2!! and the plunger moves upward until the lug III engages the periphery of the cam. The farther that the plunger is permitted to move up, the longer will be its actuating or indexing stroke when it moves down because the end of its downward movement is always the same, and is determined by the set screw 814 which. as shown in Figure 15, is in direct alignment with the end of the plunger 348.

It will be noted from Figure 6 that as the shaft 385 is indexed, it will effect a similar indexing movement of the control cam Ill. The shape of this cam is to be considered merely as illustrative for one shape oi bottle, it being understood that other cams having different shapes for producing other shapes of bottles may be substituted therefor. The shape of this cam is obtained by making the radii of each of the points around its eilective operating periphery, proportional to the corresponding radii of the bottle, and also proportional with respect to the average radius previously referred to.

A follower in the form of a roller "I is provided for engaging the periphery of this cam and the follower is attached to the end of a bell crank "I, which is plvotally mounted on a pin 1'". A spring pressed plunger Ill engages a lug 319 projecting from one arm of the bell crank to continuously urge the follower into contact with the periphery of the cam III. The arm III of the bell crank has a slot 88] formed longitudinally thereof in which is sdiustably mounted a block ill carrying a pin 8" forming a pivotal connection with a feed setting lever 8.

The lever m is pivotally connected at Ill to the stop cam SI! and is movable therewith. The lever Ill carries a clamping bolt I" which passes through a slot 801 which is circumferential with respect to center of pin Ill. so that the arm I may be swung about this center and may be clamped in any one of several positions by the clamping bolt III. The stop cam III is pivotally supported on the carrier for free swinging movement about the pin Ill. and this movement is controlled by the bell crank I'll through its pivotal connection with the pin Ill. It will be noted that the center aboutwhich the stop cam moves is in the axial plane of the plunger 3.

It was stated supra, that it could be readily determined what length of stroke the operating plunger should have to effect the unit index angle. Since this unit index angle was determined from the mean or average radius, and since this angle would have to be decreased for increases in the length 01' the radius; and increased for decreases in the length of the radius in order to keep the lengthoi' index stroke substantially constant. the length of stroke of the plunger. necessary to produce the unit or mean index angle should be halfway between its minimum and maximum strokes, Therefore, if the radius "I of the stop cam I", which is 45 irom the vertical radius ill and from the horisontal radius "I. is made of a proper proportionate length to effect the mean" index angle, then the periphery of the cam at one side of the radius I may be made of a constantly increasing radius. and the other half of a constant- 1y decreasing radius. with the result that the stroke of the plunger is gradually shortened from the radius 38! to the radius 8" to eflect decreases in the size of the index angle; and the stroke graduallyincreased from the radius 389 to the radius III to eifeet proportionate increases in the sire of the index angle.

with this as a basic set-up, and the pin "8 adjusted to make the lever arm from this pin to the center of pin 3'" equal to the arm with respect to the center of the pin are, in other words, in a 1-1 ratio, it will be apparent that a uniform indexing movement of the arbitrarily assumed length will be automatically Produced regardless of changes in the radii of control cam III.

This arbitrarily assumed length will not, of course, be suitable for all occasions, especially where roughing and feeding operations are performed on the same machine. and therefore means have been provided for varying it by adjusting the feed control lever ill relative to the stop cam ill, which thereby changes the ratio of the lever arms of the pin a: relative to the fixed pins 311 and III. This feed lever, however, eifects minute changg in the amount of feed up to a certain limit, but this limit is not great enough, and that is why the change gears 34! and'fll, shown in Figure 10, as well as the shiftable couplet lib-ill have been pro vided so that large steps of feed rate changes may be effected with this gearing and minute changes effected with the feed rate lever III.

From an operating standpoint. it will be apparent that the mechanism shown in Figure 14' 

